Heavy duty compressor or pump



2 mm EI R. BAR

INVENTOR RUDOLF BAR ATTORNEYS,

Filed Jan.

m H o HEAVY DUTY COMPRESSOR 0R PUMP HG. I

Jan. 11, 1966 United States Patent 7 Claims. a. 230-45 The present invention relates to a compressor or pump, and more particularly to a heavy-duty compressor or pump capable of producing very high pressures.

The present invention is a further development of my copending application Serial No. 265,572, filed on January 24, 1963, and entitled Turbo-Engine, the contents of the said copending application being incorporated herein by reference to the extent necessary.

The turbo-engine described in said copending application utilizes a rotary piston system in accordance with my invention which essentially consists of a rotary piston, the outer circumference of which is disposed concentrically to the axis of rotation. Raised partitioning portions are disposed within the chamber sections above the outer circumference of the rotary piston in the rear parts of the chambers as viewed in the direction of rotation. With the aid of these raised portions, a larger volume is effectively produced in a respective chamber in front thereof at the ignition moment. Simultaneously therewith, the gas is driven forwardly into the chamber by means of the raised portions with the aid of the centrifugal force. The circular or curved compression track consists above the rotary piston along the inner walls of the housing of two circular sections that intersect one another. One of the two circular sections or segments is thereby disposed coaxially to the axis of the rotary piston. The inlet and outlet are provided within this one circular section. The other circular section or segment is disposed eccentrically to the rotary piston axis. The latter circular segment or section includes or forms the curved or circular indentation by means of which is realized the compression of the gas. Depending on the degree of compression to be achieved or on Whether a plurality of engine systems are to be placed into the same circular system, curved or circular arcs or lines are added to the above-described basic layout. In the aforementioned copending application, a duct or channel system is provided through which the combustion air is conducted into the combustion spaces through appropriate check valves whereby the centrifugal forces are also utilized in the rotating piston to discharge the combustion air radially outwardly into the combustion spaces disposed about the rotary piston.

The present invention is a further development of the turbo-engine described in my application and provides a very high pressure with a medium, for example, air, by means of different cooperating compressor systems. In the system according to the present invention, the last stage for producing pressure consists of gas combustion in the explosion process. The force thus gained in the end is used for the work of a gas engine.

Accordingly, it is an object of the present invention to provide a heavy-duty compressor or pump which is simple in construction, yet capable of producing a high compression output.

It is another object of the present invention to provide a rotary heavy-duty compressor that permits high degrees of compression of the medium while simultaneously offering the possibility of a greater production of forces in the new compressor system than has been realizable heretofore.

Still a further object of the present invention resides in the provision of a heavy-duty compressor which operates ice extraordinarily economically and can be applied to great adavntage to the most varied fields of application.

Still another object of the present invention resides in the provision of a heavy-duty compressor in which the compression is realized by means of a circular column acting as rotary piston and offering advantages as regards the inertia forces.

Another object of the present invention resides in the provision of a heavy-duty compressor or pump which offers improved seals for the rotary piston operation thereof.

These and other objects, features, and advantages of the present invention will become more obvious from the following description when taken in connection with the accompanying drawing which shows, for purposes of illustration only, one embodiment in accordance with the present invention, and wherein FIGURE 1 is a transverse cross-sectional view through a heavy-duty compressor in accordance with the present invention, and

FIGURE 2 is a longitudinal axial cross-sectional view through the heavy-duty compressor of FIGURE 1.

Rotary piston systems of different types are well known in the art. However, the rotary piston system of the present invention represents a new construction for. the compressor or pump. The present invention distinguishes itself by the fact that it combines an axial compressor with a radial-type compressor as the first and second stages which precompress the medium to be compressed finally in the last stage constituted by the rotary piston of the present invention, all three stages forming an organic integral system.

As mentioned above, in my copending application describing the turbo-engine, the radial compressor was constituted by ducts, pipes or channels at or in the circular column and utilizing the centrifugal forces. In the present invention, channels in or at the circular column are used which include appropriate vanes or blades to constitute the radial compressor.

In the heavy-duty pump according to the present invention, the thus pre-compressed medium supplied by the axial and/ or radial compressor is further compressed within the chambers disposed about the rotor constituted by the circular column and provided with raised portions or embossments to be described more fully hereinafter. Poppet or check valves effectively seal the chambers with respect to the radial compressor when the pressure in the chambers exceeds the pressure in the output of the radial compressor. Additionally, the chambers are also sealed by the effect of the centrifugal forces acting on appropriate seals provided along the sliding surfaces of the rotor.

Referring now to the drawing wherein like reference numerals are used in the two views to designate like parts, the first stage of the heavy-duty compressor in accordance with the present invention is constituted by the axial compressor generally designated by reference character A and including appropriate blades or vanes suitably mounted on the rotor shaft 11 constituted by the extension of the base of the circular column generally designated by reference character C. The term circular column is used to describe the rotary piston in accordance with the present invention which is constituted by a rotor in the form of a circular column. This term has been coined to describe the present invention and utilizes the term column in its ordinary meaning. A column consists of a base, in the instant situation, forming the shaft 11, a bearer or supporting portion 12 and a capital 13 (FIGURE 2). Since the rotor is constituted by a column-like structure of substantial inertia, as viewed in cross section in FIG- URE 2, which is circular or endless as Viewed in FIGURE 1, the term circular column is used herein to describe the rotor structure. Obviously, the supporting members 12 may be spaced over the circumference, the word circular being applicable to the instant structure by reason of the continuous or endless capital structure 13.

The blade 10 of the axial compressor A may be of any known design and construction and may be suitably secured at the lateral projections or elongations of the base 11 of the circular column.

The second stage of the heavy-duty compressor in accordance with the present invention is constituted by a radial compressor or the like generally designated by reference character B. In conformity with the provision of two axial blowers A on opposite sides of the circular column, two radial compressors B are provided on opposite sides of the circular column, and more particularly, on opposite sides of the support portion 12 thereof. Each radial compressor B thereby includes suitable blades or vanes 14 appropriately mounted in any conventional manner and secured on the support portions 12. However, it is understood that the radial compressor structure need not necessarily be subdivided into two radial compressors by the bearer portion 12, but may be constituted, as in the turbo-engine described in my copending application, by the ducts, whereby only a single radial compressor system is obtained. The transition from the axial compressor into the radial compressor may take place by a diagonal-blade compressor or may be unobstructed as shown in the drawing. Conventional guide blades may also be provided wherever necessary as is well known in the art.

Since the outer circumference becomes the larger, the greater the length of the blade in the radial direction and since therewith the velocity also increases along the outer circumference with longer radii, the compressor force and the suction force increase in the direction toward the outer circumference of the circle. the discharge out of the axial compressor stage is taken over in continuous manner by the pressure and suction of the radial compressor.

The medium compressed by the radial compressor passes from the second compressor stage into the third compressor stage constituted by the rotary piston compressor by way of poppet or check valves generally designated by reference character H, of any conventional known construction, and built into the capital portion 13 of the circular column. The pre-compressed medium, such as air, is thus admitted into the chambers D disposed above the rotary piston. The valves H have the task to effectively separate the operation of the second stage from the third stage. This is realized in that high pressure produced within the compression section by the indented housing portion automatically closes the check valves H.

The chambers D disposed above the rotary piston serve for the movement of the medium while establishing the compression. As mentioned above, the chambers D are effectively limited by the outer circumference of the circular column and the inner walls of the housing generally designated by reference character 0. In the illustrated embodiment, the external housing consists of a housing portion 20 concentric to the axis of the circular column and of a housing portion 20' eccentric to the axis of rotation of the circular column to effectively provide the indentation producing the compression. Raised portions 15 are suitably provided or mounted and secured along the outer circumference of the capital portion 13 of the circular column. To enable an eifective displacement of the medium present in each chamber D without leakage, slidable sealing members generally designated by reference character K are provided within each partition wall constituted by the raised portions 15. The slidable members K are adapted to slide in the radial direction within appropriate slots or apertures provided in As a result thereof,

generally designated by reference character K in the radially outward direction to engage with the inner walls of the housing 0. Depending on the requirement, bowshaped sealing elements which are adapted to be inserted into the slidable members K may be provided as described more fully in my copending application. Additionally, the slidable members K may be suitably sealed in the radial movement thereof by means of conventional gaskets or packings having conventional clamps or clips. Since such packing seals are well known, per se, in the art, a detailed description thereof is dispensed with herein.

As mentioned above, the indented circular or curved section 20' is disposed about the chambers D to establish thereby the rotary piston compression. The concentric section 20 serves for purposes of filling the chambers B with the compressible medium. The eccentric curved section 20 intersects the circle of section 20. The radius of curvature of the indented section 20 is chosen depending on the desired degree of compression.

In order to assure a regular operation of the chambers underneath the indented wall section 20 of the housing 0, an adjusting point G is indicated at the housing and at a chamber wall. Its determination takes place in that the center of the indented portion 20' is determined. Then one-half the length of a chamber D is applied in the forward direction as seen in the normal direction of rotation from the center of the indented portion. During assembly, the indicated chamber partition wall is brought to the adjusting point G.

In the compressor utilizing the rotary piston system according to the present invention, the compression in the third stage commences at the beginning of the indented wall section 20' and continues up to the center thereof, only to decrease again afterwards. By reason of this decrease, the discharge of the medium would become irregular. In order to eliminate the same, the raised portions are mounted in the rear part of the chambers D over the capital portions 13 of the circular column. The construction of the raised portions 15 depends on the course of pressure decrease in the second half of the indented housing section 20'. Since an equalization is established with the reinforcement by the introduction of the raised portion into the rearward first arcuate section, the medium leaves evenly and with full force the circular movement. To achieve the desired results, the raised portions are provided with a gradually rising surface 15' constituting the trailing end of the chamber whereas the curved surface 15" of relatively small radius forms the forward surface of the next following chamber D of larger volume.

The highly compressed medium may be utilized from the third compressor stage as heavy-duty compressor or heavy-duty pump. Since the reinforcements in the form of raised portions on the rotor subtract from the volu metric content, the same may also be omitted and one may then proceed as follows. A pressure equalization chamber generally designated by reference character E is arranged about the indented section 20' and housing 0. A conical discharge pipe F extends through the equalization chamber E and is provided with equalization slots. The equalization is produced because within the chambers, no lower pressure can occur due to the check valve than exists below the check valves. The exchange from chamber to chamber is relatively rapid and in case of decrease of pressure in the equalization chamber E, a relatively short equalization time exists in the direction toward the slot. Additionally, a short equalization time results from the pressure in the cone pipe P which is effective in an equalizing manner with only short duration or permanence in the direction toward the apex of the cone. From the foregoing overall operation results a good, free and even discharge of the medium in full force out of the cone pipe.

The construction in accordance with the present invention permits the combination of different compressor systerms in an economic manner. The use of an axial compressor in front of a radial compressor is known per se. However, in the present system, the axial and radial compressor systems are utilized in connection with the particular third stage as described herein.

The heavy-duty compressor and pump in accordance with the present invention are characterized by the fact that very high pressures can be produced in an economic manner automatically by the use of the rotary piston method having the inner circle at the housing constituted by at least two intersecting circular sections of which one is coaxial and the other eccentric to the rotary piston axis. Furthermore, the different compressor systems may be combined into an integral unitary structure producing highest pressure in the most economical manner,

The present invention may be used as compressor, for example, with refrigerating machines, construction machines, or gas turbine and compressor units while it may be used as pump for purposes of fire extinguishers, pipe lines, mine pumps or marine pumps.

I claim:

1. A rotary piston device usable as compressor or pump and having an axis of rotation, comprising:

housing means having at least one housing section substantially concentric to said axis and another housing section eccentric to said axis, and rotor means rotating Within said housing means about said axis and constituted by a circular column,

said rotor means being provided with first means along the outer surfaces thereof to form within said housing a plurality of chambers and having radial seal means,

means for supplying a pre-compressed medium to said chambers including axial compressor means adjoined by radial compressor means both unitary with said circular column and valve means in said circular column for valving the supply of compressed medium to said chambers,

and means to enable discharge of the compressed medium from said chambers.

2. A rotary piston device according to claim 1, wherein said first means includes raised portions forming partition Walls between adjoining chambers and having relatively elongated gradually rising surfaces forming part of the rear portion of a chamber.

3. A rotary piston device according to claim 2, wherein such raised portion is provided with a circular surface of small radius of curvature forming a forward terminal surface of a respective chamber.

4. A rotary piston device according to claim 3, wherein said valve means are automatically operated check valves.

5. A rotary piston device according to claim 1, wherein said valve means are automatically operated check valves.

6. A rotary piston device according to claim 1, wherein the circular column has a base portion forming the rotor shaft, a bearer portion and an endless capital portion forming in part the boundary walls of said chambers.

7. A rotary piston device according to claim 1, further comprising equalizing chamber means above said another housing section and means including said chamber means and conical pipe means provided with slots for providing a pressure equalization.

References Cited by the Examiner UNITED STATES PATENTS 877,484 1/1908 Brooks 103110 2,349,731 5/ 1944 Hornschuch 1031 10 FOREIGN PATENTS 368,715 2/ 1923 Germany. 437,299 11/ 1926 Germany.

DONLEY I. STOCKING, Primary Examiner.

LAURENCE V. EFNER, Examiner. 

1. A ROTARY PISTON DEVICE USABLE AS COMPRESSOR OR PUMP AND HAVING AN AXIS OF ROTATION, COMPRISING: HOUSING MEANS HAVING AT LEAST ONE HOUSING SECTION SUBSTANTIALLY CONCENTRIC TO SAID AXIS AND ANOTHER HOUSING SECTION ECCENTRIC TO SAID AXIS, AND ROTOR MEANS ROTATING WITHIN SAID HOUSING MEANS ABOUT SAID AXIS AND CONSTITUTED BY A CIRCULAR COLUMN, SAID ROTOR MEANS BEING PROVIDED WITH FIRST MEANS ALONG THE OUTER SURFACES THEREOF TO FORM WITHIN SAID HOUSING A PLURALITY OF CHAMBERS AND HAVING RADIAL SEAL MEANS, MEANS FOR SUPPLYING A PRE-COMPRESSED MEDIUM TO SAID CHAMBERS INCLUDING AXIAL COMPRESSOR MEANS ADJOINED BY RADIAL COMPRESSOR MEANS BOTH UNITARY WITH SAID CIRCULAR COLUMN AND VALVE MEANS IN SAID CIRCULAR COLUMN FOR VALVING THE SUPPLY OF COMPRESSED MEDIUM TO SAID CHAMBERS, AND MEANS TO ENABLE DISCHARGE OF THE COMPRESSED MEDIUM FROM SAID CHAMBERS. 